US20150219095A1 - Sealing glove for a cylinder of a compressor, compressor and cooling appliance - Google Patents

Sealing glove for a cylinder of a compressor, compressor and cooling appliance Download PDF

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Publication number
US20150219095A1
US20150219095A1 US14/358,353 US201214358353A US2015219095A1 US 20150219095 A1 US20150219095 A1 US 20150219095A1 US 201214358353 A US201214358353 A US 201214358353A US 2015219095 A1 US2015219095 A1 US 2015219095A1
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United States
Prior art keywords
glove
compressor
sealing
cylinder
bearing
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US14/358,353
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English (en)
Inventor
Henrique Brüggmann Mühle
Dietmar Erich Bernhard Lilie
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Whirlpool SA
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Whirlpool SA
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Filing date
Publication date
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Assigned to WHIRLPOOL S.A. reassignment WHIRLPOOL S.A. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: LILIE, DIETMAR ERICH BERNHARD, MUHLE, HENRIQUE BRUGGMANN
Publication of US20150219095A1 publication Critical patent/US20150219095A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F04B39/0284—Constructional details, e.g. reservoirs in the casing
    • F04B39/0292—Lubrication of pistons or cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/14—Pistons, piston-rods or piston-rod connections
    • F04B53/143—Sealing provided on the piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • F04B35/045—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric using solenoids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/06—Cooling; Heating; Prevention of freezing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/121—Casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/126—Cylinder liners
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/008—Spacing or clearance between cylinder and piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C29/00—Bearings for parts moving only linearly
    • F16C29/02—Sliding-contact bearings
    • F16C29/025—Hydrostatic or aerostatic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
    • F16C32/0603—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a gas cushion, e.g. an air cushion
    • F16C32/0614—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a gas cushion, e.g. an air cushion the gas being supplied under pressure, e.g. aerostatic bearings
    • F16C32/0622—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a gas cushion, e.g. an air cushion the gas being supplied under pressure, e.g. aerostatic bearings via nozzles, restrictors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C37/00—Cooling of bearings
    • F16C37/002—Cooling of bearings of fluid bearings

Definitions

  • the present invention refers to a flexible glove for sealing bearing fluid channels of an aerostatic bearing compressor, more particularly aerostatic bearing compressors applied to cooling systems.
  • a cooling cycle comprises four essential elements, namely a compressor, a condenser, an expansion valve and an evaporator.
  • a cooling fluid (Freon®, for example) circulates through said components where the following operations occur.
  • the expansion valve the cooling fluid which is found originally in liquid form, expands to enter into a gaseous and rarefied form, decreasing its own temperature.
  • this fluid now with lower density, passes through an evaporator enabling it to absorb heat from the environment.
  • the fluid comes to a compressor which compresses the fluid returning it to liquid form (or compressed gaseous form).
  • the fluid passes through a condenser transmitting heat to a second environment, and these stages restart when the fluid returns to the expansion valve, thus concluding the cooling cycle.
  • Cooling compressors may present various different forms, mechanisms and functions. Each type of compressor is better adapted to a certain type of application, and a compressor model widely known in the state of the art is the linear compressor. This compressor operates by way of the axial and oscillatory movement of a piston inside a cylinder.
  • the gas that enters into a linear compressor proceeds along the following path: firstly the gas penetrates into a plenum chamber, next it passes through an inlet valve and soon after fills a region called the compression chamber, that is, a region comprised by the space between the piston and the cylinder of the compressor where there occurs compression capable of transforming it into a liquid or gas having greater density.
  • this fluid now having greater density, is displaced through a discharge valve and lastly, the fluid fills a region called the discharge chamber from where it is released for the next stages of the cooling cycle.
  • linear compressors need lubrication between the outer face of the piston and the inner face of the cylinder.
  • the purpose of said lubrication is to decrease attrition between the parts, whereby increasing the yield of the compressor and avoiding premature wear and tear of its parts. Accordingly, there are linear bearing compressors with viscous fluids, of the lubricant oil type and linear bearing compressors with gaseous fluids.
  • Linear bearing compressors with gaseous fluids are called aerostatic bearing linear compressors. Said compressors are endowed with a more efficient lubrication system than the lubrication system of the bearing compressors with viscous fluids due to the lower viscous attribution coefficient of the gaseous fluid in relation to the viscous fluid (oil).
  • Another advantage of the linear aerostatic compressor refers to the absence of an oil pump to distribute the viscous fluid inside the compressor, a fact that decreases the manufacturing cost and complexity of this product.
  • aerostatic bearing linear compressors An important characteristic of aerostatic bearing linear compressors, hereinafter referred to as aerostatic compressors, refers to the fact that they can have bearing formation through the gas from the cooling fluid itself. As they have bearing by the very cooling fluid that circulates through the compressor, this equipment saves on an extra source of lubricant, since all the lubricating fluid necessary for using these compressors is already abundantly available inside them.
  • the aerostatic bearing compressor with cooling fluid is endowed with bearing channels, located on the outer face of the cylinder. These channels are capable of distributing the gaseous fluid to distribution orifices which are spread along the cylinder.
  • the distribution orifices cross through the structure of the cylinder, meeting up with the piston region, transporting gaseous fluid homogenously to the gap existing between the cylinder and the piston.
  • sealing jacket a metal jacket having tubular geometry
  • a sealing jacket of aerostatic compressors of the state of the art is made of metal material, that is, a material having low flexibility, which requires a thorough surface finishing so that it is capable of sealing the bearing channels of the compressor.
  • the objective of the present invention is to provide a sealing system of bearing channels of aerostatic linear compressors that is simple, efficient and capable of reducing production costs of aerostatic linear compressors.
  • Another objective of the present invention is to provide a sealing glove of restriction channels of aerostatic linear compressors, the flexibility of which allows the sealing of restriction channels in aerostatic compressors, whereby preventing gas from escaping between the restriction channels.
  • a further objective of the present invention is to provide a cooling system or appliance, endowed with said sealing glove.
  • an aerostatic bearing linear compressor comprising a cylinder defined by an outer surface and an inner surface, the inner surface defining a through cavity inside the cylinder capable of enabling a linear movement of a piston in its inside, wherein the inner surface of the cylinder comprises a plurality of distribution orifices which communicate with the outer surface, the outer surface comprising bearing channels which communicate with said distribution orifices, and a sealing glove is disposed on the outer surface of the cylinder under radial tension, the association between the outer surface and the sealing glove defining restriction ducts capable of directing the bearing fluid to the distribution orifices at appropriate pressure and in the adequate quantity.
  • FIG. 1 is a longitudinal cut view of an aerostatic linear compressor of the present invention endowed with the flexible sealing glove of the present invention
  • FIG. 2 is a cross-sectional view of a flexible sealing glove of the present invention positioned on a cylinder of an aerostatic linear compressor;
  • FIG. 3 is a perspective view of a cylinder of an aerostatic linear compressor of the present invention
  • FIG. 4 is a perspective view of a cylinder of an aerostatic linear compressor endowed with a flexible sealing glove of the present invention
  • FIG. 5 is a cross-sectional view of the BB section of an aerostatic compressor linear endowed with a glove of the present invention
  • FIG. 6 is a cross-sectional view of a flexible sealing glove of the present invention.
  • FIG. 7 is a cross-sectional view of a flexible sealing glove of the present invention showing one of the potential effects of internal pressure on the bearing channels;
  • FIG. 8 is a cross-sectional view of a flexible sealing glove of the present invention showing one of the potential effects of internal pressure on the bearing channels in light of the external pressure to the flexible glove;
  • FIG. 9 is a longitudinal cut view of an aerostatic linear compressor illustrating its working during the suction stage
  • FIG. 10 is a longitudinal cut view of an aerostatic linear compressor illustrating its working during the compression stage
  • FIG. 11 is a longitudinal cut view of an aerostatic linear compressor illustrating its working during the exhaust stage
  • FIG. 12 is a longitudinal cut view of part of the compressor of the present invention in an alternative arrangement illustrating an interface region
  • FIG. 13 is a perspective view of a first alternative arrangement of the cylinder of the compressor of the present invention.
  • FIG. 14 is a perspective view of a second alternative arrangement of the cylinder of the compressor of the present invention.
  • FIG. 15 is a perspective view of a third alternative arrangement of the cylinder of the compressor of the present invention.
  • the main elements that make up an aerostatic linear compressor 200 capable of receiving the sealing glove 100 of the present invention are comprised by a piston 15 , having the function of carrying out an oscillatory movement inside a cylinder 14 ; a cylinder 14 (see FIG.
  • the piston 15 of the aerostatic compressor 200 of the present invention has bearing in the contact region between cylinder 14 and piston 15 , it is necessary that under the inner surface 4 of the cylinder 14 there be a layer of fluid preferably gaseous that reduces the attrition between these parts, decreasing the abrasion between them and increasing the yield of the compressor 200 .
  • the present invention has application in aerostatic compressors 200 which use the cooling fluid itself to perform the bearing function.
  • FIGS. 9 , 10 and 11 which illustrate the main stages of working of the compressor 200 :
  • This second portion of fluid penetrates into a passage 10 c, located on a header 10 and then follows bearing channels 1 , 2 , which direct this fluid to distribution orifices 3 which, in turn, have the function of providing a chamber of gaseous fluid between the inner surface 4 of the cylinder 14 and the outer surface of the piston 15 .
  • the compressor 200 of the present invention is endowed with bearing channels 1 , 2 , located on the outer surface 5 of the cylinder 14 , whose function is to distribute (and restrict) fluid to distribution orifices 3 , which, in turn, pass on this fluid to the gap existing between piston 15 and cylinder 14 .
  • the bearing channels 1 , 2 may present various forms and different arrangements, and may track different paths on the outer surface 5 of the cylinder 14 , such as, for example, along radial, longitudinal, helical, diagonal paths, a combination between these or any other capable of adequately performing the function (see FIGS. 13 , 14 , 15 ).
  • the sectional areas of these bearing channels 1 , 2 may also present various different forms such as, a triangular, quadrangular, rounded geometry, among others.
  • the bearing channels 1 , 2 can also be divided into feeder channels 2 and restriction channels 1 , such as illustrated in a preferred arrangement in FIG. 3 .
  • the feeder channels 2 are commonly disposed in longitudinal profiles along the cylinder 14 (see FIG. 3 ) and usually present a sectional area having greater amplitude than the sectional area of the restriction channels 1 . Said characteristic is due to the fact that the function of the feeder channels 2 is just to distribute fluid to the restriction channels 1 .
  • the restriction channels 1 also comprise the function of regulating the pressure of the fluid before it is displaced to the gap between piston 15 and cylinder 14 .
  • the restriction channels 1 are distributed in a radial arrangement along the outer face of the cylinder 14 , and usually have the capacity to communicate directly with distribution orifices 3 that release bearing fluid to the gap between piston 15 and cylinder 14 .
  • bearing channels 1 , 2 effectively fulfill the function of distributing bearing fluid in a uniform manner to the distribution orifices 3 , it is necessary that these channels 1 , 2 are sealed by some type of outer surface of the cylinder 14 that is capable of preventing the flow of fluid of a certain channel 1 , 2 from leaking to a neighboring channel 1 , 2 .
  • This sealing surface when overlapping the channels bearing formation 1 , 2 , define bearing formation ducts 1 ′, 2 ′.
  • the bearing formation ducts 1 ′, 2 ′ by presenting a closed structure (differently to the bearing channels 1 , 2 ), are effectively capable of providing fluid to the distribution orifices 3 without this fluid leaking from one channel 1 , 2 to the other channel 1 , 2 .
  • the present invention is focused on sealing these bearing channels 1 , 2 through the disposition of a flexible sealing glove 100 on the outer face 5 of the cylinder 4 , such that the sealing glove 100 maintains the cylinder 14 under radial compression.
  • the sealing glove 100 of the present invention can be defined as a substantially tubular object, having a flexible/elastic constitution capable of providing the sealing of the bearing channels 1 , 2 through a radial tension which maintains its structure in contact with the outer surface 5 of the cylinder 14 (see FIGS. 4 and 5 ).
  • the sealing glove 100 of the present invention is made of a substantially polymeric material, that is, a material that may comprise composites, polymers, elastomers and any other materials endowed with organic substances, which have average or high flexibility and which have an elasticity limit capable of enabling this sealing glove 100 to be fastened to the cylinder 14 , under radial tension, preventing the presence of gaps between the glove 100 and the cylinder 14 . Furthermore, it has to be noted that for this radial tension to occur, it is also necessary for the inner diameter of the glove 100 , when it is not tensioned, to be slightly less than the outer diameter of the cylinder 14 , whereby enabling a tensioning of the glove 100 material on the outer surface of the cylinder 14 .
  • the inner diameter of the sealing glove 100 may present, before being applied to the cylinder 14 , an inner diameter that is greater than the outer diameter of the cylinder 14 .
  • the glove 100 may be made of a thermo-contractile material, that is, a material which, once heated, contracts so as to permit installation with a tight adjustment of the sealing glove 100 on the cylinder 14 .
  • the glove 100 has benefits such as better sealing of the bearing channels 1 , 2 due to a radial tensioning of its structure around the cylinder 14 , being capable of eliminating the gaps existing between the glove 100 and the outer surface 5 of the cylinder 14 , whereby improving the process of bearing formation of the piston 15 inside the compressor 200 .
  • the flexibility of the glove 100 may potentially cause a drawback to the working of the compressor 200 .
  • Said flexibility allows the glove 100 to bend oppositely to its axial center ‘X’ in the regions comprised over the bearing channels 1 , 2 , (as can be noted in FIG. 7 ) due to the fact that the pressure existing on the bearing formation ducts 1 ′, 2 ′ is greater than the pressure on the outer side of the glove.
  • This extra source of positive pressure is exerted by the cooling fluid existing on the exhaust chamber 11 c which may act not only on the inner face of the glove 100 (running through the bearing formation ducts 1 ′, 2 ′) but also on the outer face of the glove 100 , exerting a counter pressure to the pressure existing on the bearing formation ducts 1 ′, 2 ′, whereby guaranteeing a constant flow in the bearing formation ducts 1 ′, 2 ′ (see FIG. 12 ).
  • the flexible sealing glove 100 becomes capable of sealing the bearing channels 1 , 2 , with greater effectiveness so as to avoid the leakage of fluid between said bearing channels 1 , 2 .
  • a third problem may still occur in the compressor 200 . If the pressure acting on the outer face of the glove 100 is slightly greater than the pressure acting inside the bearing formation ducts 1 ′ and 2 ′, the sealing glove 100 may bend slightly towards the central reference axis ‘X’ (see FIG. 8 ). Nevertheless, this problem can be solved by an oversizing in the section of the bearing channels 1 and 2 or even by altering the composition and/or diameter of the sealing glove 100 .
  • linear aerostatic compressor 200 as well as the flexible sealing glove 100 of the present invention may comprise various constructive alternatives, related to different forms, materials and dispositions, provided that all these alternatives comprise the conceptual part of this invention, as disclosed in this specification.
  • this polymeric sealing glove 100 dispenses with the need to perform rigorous processes on the surface finishing of the inner face of the glove 100 , and on the surface finishing of the outer face of the cylinder 14 . The elimination of such processes reduces costs, time and the complexity of production.
  • this new technology increases its efficiency and its yield. Said attributions originate from the reduction of gaps between the sealing glove 100 and the cylinder 14 that are so common in the state of the art; the decreased risk of operating failures in the compressor 200 (since the compressor 200 that uses this new technique has a lower risk of presenting malfunctions because it does not have cracks and internal deformations arising from interference coupling between the glove 100 and the cylinder 14 ); and, lastly, owing to improved distribution of bearing fluid in the gap between piston 15 and cylinder 14 thanks to the elimination of leakage between the bearing formation ducts 1 ′, 2 ′ of the compressor 200 along its extensions.
  • a compressor 200 containing the glove 100 as described may, among the most diverse applications, be used in the cooling industry.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
US14/358,353 2011-11-16 2012-11-14 Sealing glove for a cylinder of a compressor, compressor and cooling appliance Abandoned US20150219095A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
BRPI1105470-0 2011-11-16
BRPI1105470A BRPI1105470A2 (pt) 2011-11-16 2011-11-16 luva de vedação para um cilindro de um compressor, compressor e aparelho de refrigeração
PCT/BR2012/000452 WO2013071386A1 (en) 2011-11-16 2012-11-14 Sealing glove for a cylinder of a compressor, compressor and cooling appliance

Publications (1)

Publication Number Publication Date
US20150219095A1 true US20150219095A1 (en) 2015-08-06

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US14/358,353 Abandoned US20150219095A1 (en) 2011-11-16 2012-11-14 Sealing glove for a cylinder of a compressor, compressor and cooling appliance

Country Status (9)

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US (1) US20150219095A1 (es)
EP (1) EP2780597B1 (es)
JP (1) JP2014533790A (es)
KR (1) KR20140090994A (es)
CN (1) CN103946545B (es)
BR (1) BRPI1105470A2 (es)
MX (1) MX2014005793A (es)
SG (1) SG11201402268TA (es)
WO (1) WO2013071386A1 (es)

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US20140193278A1 (en) * 2011-07-04 2014-07-10 Whirlpool S.A. Adapting device for linear compressor, and compressor provided with such device
US20140234145A1 (en) * 2011-07-07 2014-08-21 Whirlpool S.A. Arrangement of components of a linear compressor
US20140241911A1 (en) * 2011-07-19 2014-08-28 Whirlpool S.A. Leaf spring and compressor with leaf spring
US20140301874A1 (en) * 2011-08-31 2014-10-09 Whirlpool S.A. Linear compressor based on resonant oscillating mechanism
US20150226203A1 (en) * 2014-02-10 2015-08-13 General Electric Company Linear compressor
US11319941B2 (en) * 2017-02-10 2022-05-03 Lg Electronics Inc. Linear compressor

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CN105626692B (zh) * 2016-03-14 2018-10-19 珠海格力节能环保制冷技术研究中心有限公司 线性压缩机及其气体轴承结构
KR102204575B1 (ko) 2018-11-09 2021-01-19 엘지전자 주식회사 리니어 압축기
WO2023272351A1 (en) * 2021-06-30 2023-01-05 Orbital Australia Pty Ltd Air compressor cylinder liner
CN116753137B (zh) * 2023-05-30 2024-04-23 烟台东德氢能技术有限公司 一种循环液封压缩气缸总成

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US5511463A (en) * 1994-10-19 1996-04-30 Stockton; Elmer A. Structure for mounting and sealing a piston sleeve within an actuator body
US6966761B1 (en) * 1999-10-21 2005-11-22 Fisher & Paykel Appliances Limited Linear compressor with aerostatic gas bearing passage between cylinder and cylinder liner
US20080008610A1 (en) * 2004-12-11 2008-01-10 Bsh Bosch And Siemens Hausgerate Gmbh Piston/Cylinder Unit
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* Cited by examiner, † Cited by third party
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JP2014533790A (ja) 2014-12-15
CN103946545A (zh) 2014-07-23
KR20140090994A (ko) 2014-07-18
SG11201402268TA (en) 2014-06-27
MX2014005793A (es) 2014-05-30
CN103946545B (zh) 2016-03-30
BRPI1105470A2 (pt) 2015-11-10
EP2780597B1 (en) 2016-07-27
WO2013071386A1 (en) 2013-05-23
EP2780597A1 (en) 2014-09-24

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